U.S. patent number 10,520,068 [Application Number 15/429,517] was granted by the patent office on 2019-12-31 for gear and an electric actuator provided therewith.
This patent grant is currently assigned to NTN Corporation. The grantee listed for this patent is NTN Corporation. Invention is credited to Yoshinori Ikeda, Hayato Kawaguchi.
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United States Patent |
10,520,068 |
Ikeda , et al. |
December 31, 2019 |
Gear and an electric actuator provided therewith
Abstract
A sintered gear and an electrical actuator with the sintered
gear where the sintered gear has spur teeth formed on a
circumference of the gear. A central hole is on the center of the
gear. A boss is formed around the central hole. A peripheral
portion is formed radially inward of the teeth. A thickness of a
region between the boss and the peripheral portion is thinner than
that of the boss. The peripheral portion is formed on at least one
side of the gear. The peripheral portion has an axially larger
thickness than the region between the boss and peripheral
portion.
Inventors: |
Ikeda; Yoshinori (Iwata,
JP), Kawaguchi; Hayato (Iwata, JP) |
Applicant: |
Name |
City |
State |
Country |
Type |
NTN Corporation |
Osaka-shi |
N/A |
JP |
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Assignee: |
NTN Corporation (Osaka-shi,
JP)
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Family
ID: |
55304205 |
Appl.
No.: |
15/429,517 |
Filed: |
February 10, 2017 |
Prior Publication Data
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Document
Identifier |
Publication Date |
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US 20170152926 A1 |
Jun 1, 2017 |
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Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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PCT/JP2015/072708 |
Aug 10, 2015 |
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Foreign Application Priority Data
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Aug 12, 2014 [JP] |
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2014-164063 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16H
25/2015 (20130101); F16H 55/17 (20130101); F16H
25/2204 (20130101); F16H 55/06 (20130101); F16H
1/20 (20130101); F16H 2025/204 (20130101); F16H
2025/2081 (20130101); F16H 2055/065 (20130101) |
Current International
Class: |
F16H
25/22 (20060101); F16H 55/17 (20060101); F16H
25/20 (20060101); F16H 55/06 (20060101); F16H
1/20 (20060101) |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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102705480 |
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Oct 2012 |
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CN |
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1 023 960 |
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Aug 2000 |
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EP |
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58-213801 |
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Dec 1983 |
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JP |
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2007-046476 |
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Feb 2007 |
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JP |
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2010-069995 |
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Apr 2010 |
|
JP |
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2011-196465 |
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Oct 2011 |
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JP |
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2012-177440 |
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Sep 2012 |
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JP |
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2013-148108 |
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Aug 2013 |
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JP |
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Primary Examiner: Elahmadi; Zakaria
Attorney, Agent or Firm: Harness, Dickey & Pierce,
P.L.C.
Parent Case Text
CROSS-REFERENCE TO RELATED APPLICATIONS
This application is a continuation of International Application No.
PCT/JP2015/072708, filed Aug. 10, 2015, which claims priority to
Japanese Application No. 2014-164063, filed Aug. 12, 2014. The
disclosures of the above applications are incorporating herein by
reference.
Claims
What is claimed is:
1. A gear formed of sintered alloy comprising: spur teeth formed on
a circumference of the gear; a central hole on the center of the
gear; a boss formed around and adjacent the central hole; a
peripheral portion is formed radially inward of and adjacent the
teeth so that a step portion, projecting directly from the
peripheral portion, is formed adjacent the teeth between the teeth
and the peripheral portion, a thickness of a region between the
boss and the peripheral portion being thinner than that of the
boss; and the peripheral portion is formed on at least one side of
the gear and has an axially larger thickness than the region
between the boss and peripheral portion, the axial thickness of the
peripheral portion and that of the boss of the gear are
substantially same, and side faces of the peripheral portion and
the boss of at least one side of the gear are substantially axially
flush with each other; a clearance amount (.delta.) between the
tooth and the peripheral portion of the gear is limited within a
range of 0.1.about.0.5 mm.
2. The gear of claim 1, wherein the width (W) of a stepped portion
from the peripheral portion to the tooth tip is set to 1.about.2
times the whole depth (H) of the tooth.
3. The gear of claim 1, wherein a plurality of lightening holes are
formed equidistantly along a circle between the peripheral portion
and the boss.
4. An electric actuator comprising: a housing; an electric motor
mounted on the housing; a speed reduction mechanism for
transmitting rotational force of the motor to a ball screw
mechanism; the ball screw mechanism converting the rotational
motion of the electric motor to the axial linear motion of a drive
shaft, the ball screw mechanism includes a nut and a screw shaft,
the nut has a helical screw groove on its inner circumference, an
output gear is secured on its outer circumference, the output gear
forms part of the speed reduction mechanism, the nut is
rotationally but axially immovably supported relative to the
housing by a pair of supporting bearings mounted on the housing,
the screw shaft has a helical screw groove on its outer
circumference corresponding to the helical screw groove of the nut,
the screw shaft is inserted into the nut via a large number of
balls, the screw shaft is axially movably but non-rotationally
supported relative to the housing; an end face of an inner ring of
one supporting bearing of the pair of supporting bearings and a
side surface of the boss closely contact each other; and the output
gear is configured by a gear defined in claim 1.
5. The electric actuator of claim 4, wherein the screw shaft is
coaxially integrated with the drive shaft.
Description
FIELD
The present disclosure relates to a sintered gear with improved
quality and to an electric actuator with a speed reduction
mechanism including the sintered gear and a ball screw mechanism.
The actuators are adapted to be used in motors in general
industries and driving sections of automobiles etc. More
particularly, the disclosure relates to an electric actuator that
converts a rotary motion from an electric motor to a linear motion
of a driving shaft, via the ball screw mechanism.
BACKGROUND
Generally, gear mechanisms, such as a trapezoidal thread worm gear
mechanism or a rack and pinion gear mechanism as a mechanism to
convert a rotary motion of an electric motor to an axial linear
motion in an electric linear actuator, are used in various kinds of
driving sections. These motion converting mechanisms involve
sliding contact portions. Thus, power loss is increased and
simultaneously size of electric motor and power consumption are
also increased. Thus, the ball screw mechanisms have been widely
used as more efficient actuators.
FIG. 7 illustrates an electric actuator utilizing a ball screw
mechanism. The electric actuator 51 includes a housing 52 with a
first housing 52a and a second housing 52b. An electric motor 53 is
mounted on the housing 52. A speed reduction mechanism 57 transmits
the rotational power of the electric motor 53 to a ball screw
mechanism 58, via a motor shaft 53a. The ball screw mechanism 58
converts the rotational motion of the electric motor 53 into the
axial linear motion of a driving shaft 59 via the speed reduction
mechanism 57. The ball screw mechanism 58 has a nut 61 formed with
a helical screw groove 61a on its inner circumference. The nut is
rotationally and axially immovably supported via supporting
bearings 66 mounted on the housing 52. A screw shaft 60 is axially
integrated with the driving shaft 59. The screw shaft 60 includes a
helical screw groove 60a on its outer circumference corresponding
to the helical screw groove 61a of the nut 61. The screw shaft 60
is inserted into the nut 61 via a plurality of balls 62 and is
axially movably but non-rotationally supported.
The electric motor 53 is mounted on the first housing 52a. A bore
63a and a blind bore 63b are formed, respectively, in the first and
second housings 52a, 52b to contain the screw shaft 60. The speed
reduction mechanism 57 has an input gear 54, secured on the motor
shaft 53a, an intermediate gear 55 and an output gear 56, secured
on the nut 61, and mating with the intermediate gear 55.
A gear shaft 64 is supported on the first and second housings 52a,
52b. Bushes 65, of synthetic resin, are interposed in either one or
both of the spaces between the gear shaft 64 and intermediate gear
55 or between the first and second housings 52a, 52b and the gear
shaft 64. Thus, the intermediate gear 55 can be rotationally
supported relative to the housing 52. Accordingly, it is possible
to provide an electric actuator 51 that can interrupt or reduce the
transmission of vibration caused by play between the intermediate
gear 55 and the gear shaft 64 as well as by play of gear shaft 64
itself. (See, JP2013-148108 A)
In the prior art electric actuator 51, the rotational power of the
electric motor 53 is transmitted to the nut 61, of the ball screw
mechanism 58, via the speed reduction mechanism 57, including the
input gear 54, the intermediate gear 55 and the output gear 56. The
nut 61 is rotationally supported by a pair of the supporting
bearings 66 with deep groove ball bearings. The output gear 56 is
arranged between the two supporting bearings 66 and secured on the
nut 61, via a key. The output gear 56 contacts an inner ring 67 of
one of the supporting bearings 66.
The inner rings 67 of the bearings 66 are secured on the outer
circumference of the nut 61 and thus rotate together with the nut
61. On the other hand, the outer rings 68 of the bearings 66 cannot
rotate since they are securely fit in the housing 52. Accordingly,
smooth rotation of the output gear 56 would be impaired if the side
surface of the output gear 56 contacts the end face of the outer
ring 68 of the bearing 66. Thus, the output gear 56 is formed so
that its axial thickness is smaller than its boss 56a that contacts
the inner ring 67 of the bearing 66. This prevents contact of the
output gear 56 against the outer ring 68 of the bearing 66.
Accordingly, the output gear 56 is formed so that its axial
thickness is small except for its boss 56a, as shown in FIG. 8(b).
In the output gear 56, with such a configuration, only the boss 56a
contacts a supporting surface 69. The tooth tip portion 56b does
not contact the supporting surface 69 when the output gear 56 is
placed on the supporting surface 69 during manufacturing of the
output gear 56. Accordingly, it is believed that a bow is created
in the tooth tip portion 56b, as shown by an arrow in FIG. 9. This
would impair the manufacturing accuracy of the output gear 56.
Especially in the case of a gear made of sintered alloy, such as
the prior art output gear 56 used in the electric actuator 51, the
configuration of the output gear 56 would deform under its own
weight due to an insufficiency of the binding degree of powder for
a time until desired strength has been obtained after completion of
the sintering treatment in the manufacturing processes. In
addition, corners of teeth of the sintered output gear 56 tend to
be damaged. Thus, a problem exists that damage occurs to the teeth
caused by interference of the teeth tips 56b with a surface 69 of a
supporting table due to vibrations during transfer of the gears 56
in a laid down state just after their compaction during
manufacturing steps.
SUMMARY
It is, therefore, an object of the present disclosure to provide a
sintered gear with improved quality that can prevent tooth damage
and deformation, such as bow of the teeth, during manufacturing
steps of the sintered gear. An electric actuator would be provided
with such a sintered gear.
To achieve the object of the present disclosure, a gear formed of
sintered alloy comprises spur teeth formed on a circumference of
the gear. A central hole is on the center of the gear. A boss is
formed around the central hole. A peripheral portion is formed
radially inward of the teeth. A thickness of a region between the
boss and the peripheral portion is thinner than that of the boss.
The peripheral portion is formed on at least one side of the gear
and has an axially larger thickness.
The spur teeth are formed on a circumference of the gear. A central
hole is on the center of the gear. A boss is formed around the
central hole. A peripheral portion is formed radially inward of the
teeth. A thickness of a region between the boss and the peripheral
portion is thinner than that of the boss. The peripheral portion is
formed on at least one side of the gear and has an axially large
thickness. Thus, it is possible to easily form a gear with a
desired exact configuration and dimension even though it has a
complicated configuration requiring high manufacturing accuracy.
Also, it is possible to prevent gear teeth from being damaged due
to interference of the teeth tips with a surface of a supporting
table during motion or transfer of the gears. Additionally, gear
teeth damage is prevented due to deformation caused by the weight
of gear itself even if the binding degree of powder is
insufficient. In addition, it is possible to prevent an accuracy
degradation of the gear caused by contact of not only the boss but
also the peripheral portion near the teeth tips against the
supporting table when the gear is laid on the table during the
manufacturing steps. Thus, it is also possible to provide a gear
with improved quality.
The axial thickness of the peripheral portion and that of the boss
of the gear are substantially same. Side faces of the peripheral
portion and the boss of at least one side of the gear are
substantially axially flush with each other.
The clearance amount between the tooth and the peripheral portion
of the gear is limited within a range of 0.1.about.0.5 mm. This
makes it possible to protect the tooth tip of the gear. Also, it
keeps the suppress variation of the density of each part of the
gear, due to variation of compaction distance in sintering, to a
minimum.
A width of a stepped portion from the peripheral portion to the
tooth tip is set to 1.about.2 times the entire depth of the tooth.
This makes it possible to prevent the bow of the tooth tip portion
due to deformation of the peripheral portion even if the gear is
laid on a table.
A plurality of lightening holes are formed equidistantly along a
circle between the peripheral portion and the boss. This keeps the
strength and rigidity while reducing the weight of the gear.
An electric actuator comprises a housing, an electric motor mounted
on the housing, a speed reduction mechanism and ball screw
mechanism. The ball screw mechanism is able to convert the
rotational motion of the electric motor to the axial linear motion
of a drive shaft. The ball screw mechanism includes a nut and a
screw shaft. The nut is formed with a helical screw groove on its
inner circumference. The nut has an output gear secured on its
outer circumference. The output gear forms part of the speed
reduction mechanism. The nut is rotationally but axially immovably
supported relative to the housing by a pair of supporting bearings
mounted on the housing. The screw shaft is formed with a helical
screw groove on its outer circumference that corresponds to the
helical screw groove of the nut. A large number of balls are
inserted into the nut. The shaft is axially movably but
non-rotationally supported relative to the housing. An end face of
an inner ring of one supporting bearing, of the pair of supporting
bearings, and a side surface of the boss closely contact each
other. The output gear is configured by a gear defined above
The electric actuator comprises a housing, an electric motor
mounted on the housing, a speed reduction mechanism and a ball
screw mechanism. The ball screw mechanism is able to convert the
rotational motion of the electric motor to the axial linear motion
of a drive shaft. The ball screw mechanism includes a nut and a
screw shaft. The nut is formed with a helical screw groove on its
inner circumference. An output gear is secured on its outer
circumference. The output gear forms part of the speed reduction
mechanism. The nut is rotationally but axially immovably supported
relative to the housing by a pair of supporting bearings mounted on
the housing. The screw shaft is formed with a helical screw groove
on the outer circumference corresponding to the helical screw
groove of the nut. A large number of balls are inserted into the
nut. The shaft is axially movably but non-rotationally supported
relative to the housing. An end face of an inner ring of one
supporting bearing of the pair of supporting bearings and a side
surface of the boss closely contact each other. The output gear is
configured by a gear defined above. Thus, it is possible to provide
an electric actuator with improved quality that can achieve smooth
rotation of the output gear. This prevents gear teeth damage and
gear bow which would be caused during manufacture of the sintered
gear.
The gear of the present disclosure comprises spur teeth formed on a
circumference of the gear. A central hole is on the center of the
gear. A boss is formed around the central hole. A peripheral
portion is formed radially inward of the teeth. A thickness of a
region between the boss and the peripheral portion is thinner than
that of the boss. The peripheral portion is formed on at least one
side of the gear and has an axially larger thickness. Thus, it is
possible to easily form a gear with a desired exact configuration
and dimensions even though it has a complicated configuration
requiring high processing accuracy. Also, it is possible to prevent
the gear teeth from being damaged due to interference of the teeth
tips with a surface of a supporting table during motion or transfer
of the gears. Additionally, deformation is prevented that would be
caused by the weight of the gear itself even if the binding degree
of powder is insufficient. In addition, it is possible to prevent
accuracy degradation of the gear, caused by contact of not only the
boss but also the peripheral portion near the teeth tips against
the supporting table, when the gear is laid on the table during the
manufacturing steps. Thus, it is also possible to provide a gear
with improved quality.
The electric actuator of the present disclosure comprises a
housing, an electric motor mounted on the housing, a speed
reduction mechanism and a ball screw mechanism. The ball screw
mechanism is able to convert the rotational motion of the electric
motor to the axial linear motion of a drive shaft. The ball screw
mechanism includes a nut and a screw shaft. The nut is formed with
a helical screw groove on its inner circumference. An output gear
is secured on its outer circumference. The output gear forms part
of the speed reduction mechanism. The nut is rotationally but
axially immovably supported relative to the housing by a pair of
supporting bearings mounted on the housing. The screw shaft is
formed with a helical screw groove on the outer circumference that
corresponds to the helical screw groove of the nut. A large number
of balls are inserted into the nut. The nut is axially movably but
non-rotationally supported relative to the housing. An end face of
an inner ring of one supporting bearing of the pair of supporting
bearings and a side surface of the boss closely contact each other.
The output gear is configured by a gear defined above. Thus, it is
possible to provide an electric actuator with improved quality that
can achieve smooth rotation of the output gear. Also, it prevents
gear teeth damage and gear bow that would be caused during
manufacture of the sintered gear.
Further areas of applicability will become apparent from the
description provided herein. The description and specific examples
in this summary are intended for purposes of illustration only and
are not intended to limit the scope of the present disclosure.
DRAWINGS
The drawings described herein are for illustrative purposes only of
selected embodiments and not all possible implementations, and are
not intended to limit the scope of the present disclosure.
FIG. 1 is a longitudinal section view of one embodiment of an
electric linear actuator of the present disclosure.
FIG. 2 is an enlarged longitudinal section view of the ball screw
mechanism of FIG. 1.
FIG. 3 is a perspective view of an output gear of the present
disclosure.
FIG. 4 is a partially enlarged view of a contact portion between
the output gear of FIG. 1 and a supporting bearing.
FIG. 5(a) is an explanatory view of a state of the output gear of
FIG. 1 laid on a supporting table.
FIG. 5(b) is a partially enlarged view of a tooth tip of the output
gear of FIG. 5(a).
FIG. 6 is an explanatory view of relations of dimensions of the
tooth tip of FIG. 5.
FIG. 7 is a longitudinal section view of a prior art electric
linear actuator.
FIG. 8(a) is a plan view of the output gear of FIG. 7.
FIG. 8(b) is a front view of the output gear of FIG. 8(a).
FIG. 9 is an explanatory view of a state of the output gear of FIG.
7 laid on a supporting table.
DETAILED DESCRIPTION
Hereafter, embodiments of the present disclosure will be
specifically described with reference to the attached drawings.
A mode for carrying out the present invention has an electric
actuator that includes a housing, an electric motor mounted on the
housing, a speed reduction mechanism and a ball screw mechanism.
The ball screw mechanism converts the rotational motion of the
electric motor to the axial linear motion of a drive shaft. The
ball screw mechanism includes a nut and a screw shaft. The nut is
formed with a helical screw groove on its inner circumference. An
output gear is secured on its outer circumference. The output gear
forms part of the speed reduction mechanism. The nut is
rotationally but axially immovably supported relative to the
housing by a pair of supporting bearings mounted on the housing,
The screw shaft is formed with a helical screw groove on its outer
circumference that corresponds to the helical screw groove of the
nut. A large number of balls are inserted into the nut. The shaft
is axially movably but non-rotationally supported relative to the
housing. The speed reduction mechanism includes an intermediate
gear mating with an input gear secured on a motor shaft of the
electric motor. The output gear integrally secured on the nut forms
a part of the ball screw mechanism. An end face of an inner ring of
one supporting bearing of the pair of supporting bearings and a
side surface of the boss closely contact each other. The output
gear is formed of sintered alloy. The output gear has spur teeth
formed on the circumference of the output gear. A central hole is
on the center of the output gear. A boss is formed around the
central hole. A peripheral portion is formed radially inward of the
teeth. A thickness of a region between the boss and the peripheral
portion is thinner than other portions of the output gear. A
plurality of lightening holes is formed equidistantly along a
circle between the peripheral portion and the boss. The axial
thickness of the peripheral portion and that of the boss of the
gear are substantially the same. Side faces of the peripheral
portion and the boss of at least one side of the gear are axially
flush with each other.
FIG. 1 is a longitudinal section view of one preferable embodiment
of an electric linear actuator of the present disclosure. FIG. 2 is
an enlarged longitudinal section view of the ball screw mechanism
of FIG. 1. FIG. 3 is a perspective view of an output gear of the
present disclosure. FIG. 4 is a partially enlarged view of a
contact portion between the output gear of FIG. 1 and a supporting
bearing. FIG. 5(a) is an explanatory view of a state of the output
gear of FIG. 1 laid on a supporting table. FIG. 5(b) is a partially
enlarged view of a tooth tip of the output gear of FIG. 5(a). FIG.
6 is an explanatory view of relations of dimensions of the tooth
tip of FIG. 5.
As shown in FIG. 1, the electric actuator 1 includes a cylindrical
housing 2, an electric motor M mounted on the housing 2, a speed
reduction mechanism 6 and a ball screw mechanism 8. The speed
reduction mechanism 6 includes an intermediate gear 4 mating with
an input gear 3 mounted on a motor shaft 3a of the electric motor
M. An output gear 5 mates with the intermediate gear 4. The ball
screw mechanism 8 converts rotational motion of the electric motor
M to axial linear motion of a driving shaft 7, via the speed
reduction mechanism 6.
The housing 2 is formed of aluminum alloy such as A 6063 TE, ADC 12
etc. by die casting. The housing 2 includes a first housing 2a and
a second housing 2b. The second housing 2b abuts and is bolted to
an end face of the first housing 2a. The electric motor M is
mounted on the first housing 2a. The first housing 2a and the
second housing 2b are formed with a through bore 11 and a blind
bore 12, respectively, to contain the screw shaft 10, coaxially
integrated with the drive shaft 7.
The input gear 3 is press-fit onto the end of the motor shaft 3a of
the electric motor M. The motor shaft 3a is rotationally supported
by a rolling bearing 13. The bearing 13 is a deep groove ball
bearing mounted on the second housing 2b. The output gear 5, mating
with the intermediate spur gear 4, is integrally secured on a nut
18, forming part of the ball screw mechanism 8, via a key 14.
The drive shaft 7 is integrally formed with a screw shaft 10,
forming part of the ball screw mechanism 8. Guide pins 15, 15 are
mounted on one end (right-side end in FIG. 1) of the drive shaft 7.
A sleeve 17 is fit in the blind bore 12 of the second housing 2b.
The inner circumference of the sleeve 17 includes axially extending
recessed grooves 17a, 17a. The sleeve grooves 17a, 17a are formed
by grinding. The recessed grooves 17a, 17a are circumferentially
oppositely arranged. The guide pins 15, 15 engage the grooves 17a,
17a to axially movably support but not rotationally support the
screw shaft 10. Falling-out of the sleeve 17 can be prevented by a
stopper ring 9 mounted on an opening of the blind bore 12 of the
second housing 2b.
The sleeve 17 is formed from a sintered alloy by an injection
molding machine for molding plastically prepared metallic powder.
In this injection molding, metallic powder and binder, comprised of
plastics and wax, are firstly mixed and kneaded by a mixing and
kneading machine to form pellets from the mixed and kneaded
material. The pellets are fed into a hopper of the injection
molding machine. The pellets are then pushed into dies under a
heated and melted state and finally formed into the sleeve by a
so-called MIM (Metal Injection Molding) method. The MIM method can
easily mold sintered alloy material into articles having desirable
accurate configurations and dimensions even though the articles
require high manufacturing technology and have hard to form
configurations.
On the other hand, the guide pins 15 are formed of high carbon
chromium bearing steel such as SUJ 2 or carburized bearing steel
such as SCr 435. Their surfaces are formed with a carbonitrided
layer having carbon content of more than 0.80% by weight and a
hardness of more than 58 HRC. In this case, it is possible to adopt
needle rollers used in needle bearings as guide pins 15. This makes
it possible to have the guide pins 15 with a hardness of HRC 58 or
more. Also, the pins 15 have excellent anti-wear property,
availability and manufacturing cost.
As shown in the enlarged view of FIG. 2, the ball screw mechanism 8
includes the screw shaft 10 and the nut 18, inserted on the screw
shaft 10 via balls 19. The screw shaft 10 is formed, on its outer
circumference, with a helical screw groove 10a. It is axially
movably but not rotationally supported. On the other hand, the nut
18 is formed, on its inner circumference, with screw groove 18a
that corresponds to the screw groove 10a of the screw shaft 10. A
plurality of balls 19 is rollably contained between the screw
grooves 10a, 18a. The nut 18 is axially immovably but rotationally
but supported by the two supporting bearings 20, 20 relative to the
housings 2a, 2b. A numeral 21 denotes a bridge member to achieve an
endless circulating passage of balls 19 through the screw groove
18a of the nut 18.
The cross-sectional configuration of each screw groove 10a, 18a may
be either one of circular-arc or Gothic-arc configuration. However,
the Gothic-arc configuration is adopted in this embodiment. It has
a large contacting angle with the balls 19 and sets a small axial
gap. This provides large rigidity against the axial load and thus
suppresses the generation of vibration.
The nut 18 is formed of case hardened steel such as SCM 415 or SCM
420. Its surface is hardened to HRC 55.about.62, by vacuum
carburizing hardening. This omits treatments, such as buffing, for
scale removal after heat treatment and reduces the manufacturing
cost. On the other hand, the screw shaft 10 is formed of medium
carbon steel such as S55C or case hardened steel such as SCM 415 or
SCM 420. Its surface is hardened to HRC 55.about.62, by induction
hardening or carburizing hardening.
The output gear 5, forming part of the speed reduction mechanism 6,
is firmly secured on the outer circumference 18b of the nut 18, via
a key 14. The support bearings 20, 20 are press-fit onto the nut
18, via a predetermined interference, at both sides of the output
gear 5. More particularly, the output gear 5 is secured on the nut
18 by the key 14. It is fit in a rectangular space formed by a key
way 14a on an outer circumference 18b of the nut 18 and a key way
32a on an inner circumference of the output gear 5. This prevents
both the supporting bearings 20, 20 and output gear 5 from axially
shifting even though strong thrust loads are applied to them from
the drive shaft 7. Each supporting bearing 20 is a deep groove ball
bearing. Both sides include mounted shield plates 20a, 20a to
prevent lubricating grease, sealed within the bearing body, from
leaking outside and abrasive debris from entering into the bearing
body from the outside.
In the present embodiment, both the supporting bearings 20, 20 are
formed by deep groove ball bearing having the same specifications.
Thus, it is possible to support both a thrust load, applied from
the driving shaft 7, and a radial load, applied from the output
gear 5. Also, this simplifies confirmation work to prevent errors
during assembly of the bearing. Thus, this improves the assembling
operability. In this case, the term "same specifications" means
that the deep groove ball bearings have the same inner diameters,
outer diameters, width dimensions, rolling element sizes, rolling
element numbers and internal clearances.
One of the pair of supporting bearings 20, 20 is mounted on the
first housing 2a via a washer 22. The washer 22 is a ring-shaped
elastic member. The washer 22 is a wave washer press-formed from
austenitic stainless steel (JIS SUS 304 etc.) or preserved cold
rolled steel sheet (JIS SPCC etc.). It has high strength and wear
resistance. An inner diameter D of the washer 22 is larger than an
outer diameter d of the inner ring 23 of the supporting bearing 20.
This eliminates axial play of the pair of supporting bearings 20,
20. Thus, smooth rotation of the nut 18 is obtained. In addition,
the washer 22 contacts only the outer ring 24 of the supporting
bearing 20. The washer 22 does not contact the rotational inner
ring 23. Thus, it is possible to prevent the inner ring 23 of the
supporting bearing 20 from contacting the housing 2a even if the
nut 18 is urged toward the housing 2a by a reverse-thrust load.
Thus, this prevents the nut 18 from being locked by an increase of
frictional force.
As shown in FIG. 1, a gear shaft 25 for the intermediate gear 4,
forming part of the speed reduction mechanism 6, is fit in the
first and second housings 2a, 2b. The intermediate gear 4 is
rotationally supported on the gear shaft 25, via a rolling bearing
26. When press-fitting one end (first housing 2a-side end) of the
gear shaft 25 into the first housing 2a, it is possible to allow
assembling misalignment. Thus, smooth rotational performance by
performing the clearance fitting of the other end (second housing
2b-side end) may be obtained. The rolling bearing 26 is formed from
a needle roller bearing of a so-called shell type. It includes an
outer ring 27 and a plurality of needle rollers 29 press-formed
from steel sheet and press-fit into an inner circumference of the
intermediate gear 4. The plurality of needle rollers 29 are
rollably contained in the outer ring 27 via a cage 28. This enables
the adoption of easily or readily available bearings or a standard
design and thus reduces manufacturing cost.
Ring-shaped washers 30, 30 are installed on both sides of the
intermediate gear 4. The washers 30, 30 prevent direct contact of
the intermediate gear 4 against the first and second housings 2a,
2b. In this embodiment, the face width of the teeth 4a of the
intermediate gear 4 is smaller than an axial width of the gear
blank. This reduces contact area between the intermediate gear 4
and the washers 30, 30. Thus, their frictional resistance is
reduced and smooth rotational performance is obtained. The washers
30 are flat washers press-formed of austenitic stainless steel
sheet or preserved cold rolled steel sheet. They have high strength
and frictional resistance. Alternatively, the washers 30 may be
formed of brass, sintered metal or thermoplastic synthetic resin
such as PA (polyamide) 66, where a predetermined amount of fiber
reinforcing material such as GF (glass fibers) is impregnated.
The output gear 5 is formed from a sintered alloy. It includes spur
teeth 5a on its circumference and a central (circular) hole 5b. The
hole 5b is adapted to be fit onto the outer circumference 18b of
the nut 18. A plurality of lightening holes 33 are formed in a
middle portion 34 equidistantly along a circle between a peripheral
portion 31, near the teeth 5a, and a boss 32 near the central hole
5b. The key way 32a engages the securing key 14. The key way 32a is
formed on the inner circumference of the boss 32. Although it is
illustrated with circular lightening holes 33, the shape of each
hole 33 is not limited to a circle. Any other shape, an egg-shape
or a triangle with a configuration expanding radially outward may
be possible. The lightening holes 33 reduce the weight of the
output gear 5 while keeping the strength and rigidity of the output
gear 5.
Metallic powder for the sintering alloy comprises completely
alloyed powder Fe, Mo, Ni (atomized iron powder of alloyed and
melted steel where alloyed components are uniformly distributed in
the grains) or partially alloyed powder (alloyed powder where
partially alloyed powder is adhered to pure iron powder). One
example of the alloyed powders is a hybrid type alloyed powder
(trade name JIP 21 SX of JFE steel Co., Japan) where pre-alloy
copper powder with Fe of 2% by weight, Ni of 1% by weight and Mo is
adhered to fine Ni powder, Cu powder and graphite powder via a
binder. This hybrid type alloyed powder is able to obtain high
mechanical strength (tensioning strength and hardness) due to an
increase of martensite phase ratio to the metallic structure of the
sintered body while increasing the cooling speed (higher than
50.degree. C./min) after sintering. This eliminates heat treatment
after sintering and thus provides an output gear with high
accuracy. It is preferable Mo of 0.5.about.1.5% by weight in order
to improve the hardenability and Ni of 2.about.4% by weight is
added in order to improve the toughness of a sintered body.
Similarly to the sleeve 17 described above, the output gear 5 may
be formed of sintered alloy by an MIM method by preparing the
metallic powder plastically.
As shown in FIG. 5(a), the axial thickness of the peripheral
portion 31, near the teeth 5a, and that of the boss 32, near the
central hole 5b of the gear 5, are substantially the same. Side
faces of the peripheral portion 31 and the boss 32 of the gear 5
are substantially axially flush with each other. The axial
thickness of the middle portion 34 between the peripheral portion
31 and a boss 32 is set thinner. The terms "substantially same" and
"substantially axially flush" in the specification mean only target
values in design and thus errors caused by machining should be
naturally allowed.
The output gear 5 with such structure enables the end face of the
inner ring 23 of the supporting bearing 20 rotating together with
the nut 18 to closely contact the side surface of the boss 32 of
the output gear 5. The outer ring 24 of the stationary side is
separated from the side surface of the boss 32 as shown in FIG. 4.
Thus, smooth rotation of the output gear 5 can be assured.
In addition, the axial thickness of the peripheral portion 31, near
the teeth 5a, and that of the boss 32, near the central hole 5b of
the gear 5, are substantially the same. The side faces of the
peripheral portion 31 and the boss 32 of the gear 5 are
substantially axially flush with each other. Thus, not only the
boss 32 but also the peripheral portion 31 contact a surface of a
supporting table 35, as shown in FIG. 5(b). This occurs when the
gear 5 is laid on the supporting table during manufacturing steps
of the gear 5. Accordingly, it is possible to prevent damage to the
gear teeth 5a. Thus, accuracy degradation is prevented due to
interference of the teeth 5a with the surface of the supporting
table that would occur by deformation of the gear 5 by its own
weight even if the binding degree of powder is insufficient.
In addition, problems in the output gear 5, formed of sintered
alloy of this kind, exists in that variation of the density of each
part of the gear 5 tends to be generated due to variation of a
compaction distance (pressing distance) during sintering. This
occurs when a clearance amount .delta. of a stepped portion 36
between the end face of the tooth 5a and the side surface of the
peripheral portion 31 is set too large, as shown in FIG. 6. Thus,
according to the present embodiment, the clearance amount .delta.
between the tooth 5a and the peripheral portion 31 of the gear 5 is
limited within a range of 0.1.about.0.5 mm. This protects the tip
ends of the teeth 5a and suppresses variation of the density of
each part of the gear.
Furthermore, a width W of the stepped portion 36 from the
peripheral portion 31 to the tooth tip is set to 1.about.2 times
the entire depth H of the tooth 5a (W=1.about.2H). This prevents a
bow of the tooth tip portion due to deformation of the peripheral
portion 31 even if the gear 5 is laid on the supporting table.
Although shown in the exemplified embodiment that the output gear 5
where the axial thickness of the peripheral portion 31, near the
teeth 5a, and that of the boss 32, near the central hole 5b of the
gear 5, are substantially same, and both side faces of the
peripheral portion 31 and the boss 32 of the gear 5 are
substantially axially flush with each other, the present disclosure
is not limited to such an embodiment. Accordingly, it may be
possible to arrange so that side faces of the peripheral portion 31
and the boss 32 of at least one side of the gear 5 are
substantially axially flush with each other. At least the boss 32
contacting the side surface of the inner ring 23 is formed thicker
so as to achieve that the outer ring 24 of the supporting bearing
20 does not contact with the side face of the boss 32 of the output
gear 5.
In addition, the side faces of the peripheral portion 31, near the
teeth 5a, and the boss 32, near the central hole 5b, do not
necessarily have to be flat all along their circumference. At least
the side face of boss 32 may be an uneven surface so that oil films
of lubrication grease can be easily formed in order to prevent
fretting of the contact surfaces between the boss 32 and the inner
ring 23 of the supporting bearing 20.
The electric actuator of the present disclosure can be used on
electric motors for a general industry use, driving portions of an
automobile etc. and applied to an actuator provided with a ball
screw mechanism that converts a rotational input motion from an
electric motor to a linear motion of a drive shaft via a gear
reduction mechanism.
The present disclosure has been described with reference to the
preferred embodiments. Obviously, modifications and alternations
will occur to those of ordinary skill in the art upon reading and
understanding the preceding detailed description. It is intended
that the present disclosure be construed to include all such
alternations and modifications insofar as they come within the
scope of the appended claims or their equivalents.
* * * * *